US3731903A - Ball canister and system for controlling cavitation in liquids - Google Patents

Ball canister and system for controlling cavitation in liquids Download PDF

Info

Publication number
US3731903A
US3731903A US00095044A US3731903DA US3731903A US 3731903 A US3731903 A US 3731903A US 00095044 A US00095044 A US 00095044A US 3731903D A US3731903D A US 3731903DA US 3731903 A US3731903 A US 3731903A
Authority
US
United States
Prior art keywords
canister
balls
case
cavitation
control valve
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
US00095044A
Other languages
English (en)
Inventor
A Webb
J Tullis
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
FOWLER KNOBBE AND MARTENS
Original Assignee
Individual
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Individual filed Critical Individual
Application granted granted Critical
Publication of US3731903A publication Critical patent/US3731903A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15D—FLUID DYNAMICS, i.e. METHODS OR MEANS FOR INFLUENCING THE FLOW OF GASES OR LIQUIDS
    • F15D1/00—Influencing flow of fluids
    • F15D1/02—Influencing flow of fluids in pipes or conduits

Definitions

  • a ball canister having a hollow case with [22] Filed: an inlet and an outlet, the case having a portion which is frustoconical and is filled with tightly packed balls, with the diameter and length of the ball filled case [21] Appl. No.2 95,044
  • portion being sized to significantly repress cavitation v in a liquid flow system into which the canister is to be inserted, either alone or in conjunction with a control valve.
  • a sizing method is disclosed and a particular construction example is explained for a high pressure water system.
  • This invention relates to apparatus for controlling or repressing cavitation in a flowing liquid, and has particular reference to a ball canister and further reference to the ball canisters cooperation with a control valve in a liquid flow system.
  • Cavitation generally refers to the formation, growth and collapse of vapor cavities in liquid as the pressure is reduced to near or below the vapor pressure of the liquid by the flow conditions.
  • the pressure reduction necessary to cause cavitation can originate from accelerating the liquid or from non-streamlined flow. In the latter case, turbulent eddies are created and the pressure reduction at the core of the turbulent eddies can be of sufficient magnitude to produce cavitation even when the average pressure in the liquid stream is considerably higher than the vapor pressure of the liquid.
  • a critical liquid velocity can be determined empirically at which cavitation is insipient at a given pressure.
  • the cavitation may vary from light to heavy and from fine grained to coarse, or the system may go into supercavitation wherein the full stream is vaporized.
  • the vapor cavities move downstream, become unstable and collapse, with the implosion of the cavitation bubbles creating extremely high local pressures which can be on the order of 10 to psi.
  • the growth and collapse cycle of a vapor cavity can be of very short duration, such that cavitation can form and collapse inside a valve, turbine or other valuable structure thereby pitting and eroding the structure which caused it; or, depending on many variables and the degree of cavitation, the cavities may collapse within the stream or downstream against another structure.
  • the vaporized zone may extend many feet downstream before collapsing.
  • the extremely high collapse pressures of cavitation bubbles can constitute an enormous and earth-shaking destructive force wrecking havoc with the hydraulic system and structures while creating sonic and vibratory levels of such magnitude that it is uncomfortable to be in the near vicinity, and at lesser magnitudes can constitute an insidious eroding force on expensive hydraulic equipment, or a useful phenomenon for cleaning, for mixing and homogenizing of liquid, or for the breakdown or synthesis of chemicals.
  • the presence of cavitation can produce undesirable pressure and flow variations and can reduce the efficiency of turbines, pumps and control valves.
  • ball canisters or devices resembling ball canisters have been used in gas systems as early as 1917, for example as illustrated in British Pat. No. 112,980 to Briggs et al., and have been used in water systems as early as 1398, for example as illustrated in British Pat. No. 24,148 to Hurst, so far as is known there has been no specific ap plication of ball canisters to the phenomenon of cavitation in flowing liquids, nor has the structure of ball canisters been particularly suitable for this purpose.
  • a ball canister if properly constructed will serve to receive the liquid stream at high pressure and discharge the liquid at a relatively low pressure while controlling or repressing cavitation in the liquid.
  • a canister comprises a case having an inlet and outlet, a plurality of balls filling the case along at least a portion of the length thereof, and means retaining the balls in the case.
  • the balls are small relative to the diameter of the case so that it requires many balls to fill a cross-section of the case, and the case diameter and the case length portion filled by the balls are sized to significantly limit the occurance of cavitation in the liquid stream passing through the ball volume at the maximum designed volume flow rate of the system. The sizing depends upon the system requirements and the results desired.
  • the canister case includes a tapered portion which gradually increases in diameter in the direction from the inlet toward the outlet, the balls are tightly packed in the tapered portion, and in one or more layers at the upstream end of the ball volume, the balls are welded together.
  • the tapered construction maximizes the pressure reduction afforded by each layer of balls in relation to critical cavitation velocities of the liquid at the local pressures, thereby greatly reducing both the number of balls and the length of the canister while increasing its efficiency.
  • the diameter of the canister case at the upstream end of the packed balls is made sufficiently small to present a liquid velocity at the first layer of packed balls near the incipient cavitation velocity at the maximum designed volume flow rate of the system.
  • a system for supplying liquid at a relatively low pressure from a high pressure supply while repressing cavitation in the liquid comprises a control valve connected to the high pressure supply and a ball canister connected on the outlet or downstream side of the control valve.
  • the case diameter and the case length portion containing the ball volume are sized to significantly suppress cavitation at the control valve over a range of volume flow rates which includes the designed maximum volume flow rate of the system.
  • the control valve includes an operator responsive to a hydraulic condition in the system, and means for sensing the hydraulic condition downstream of the packed balls in the canister.
  • FIG. 1 is a side elevation of a high pressure testing installation in a water system, illustrating the ball canister operating in conjunction with a control valve;
  • FIG. 2 is a graph illustrating cooperation of the ball canister and the control valve at different degrees of opening of the valve
  • FIG. 3 is a graph illustrating the empirical determination of cavitation in a given system
  • FIG. 4 is a modified longitudinal sectional view of the ball canister proper of FIG. 1;
  • FIG. 5 is a sectional view taken along line 5-5 of FIG. 4;
  • FIG. 6 is a fragmentary sectional view taken along line 66 of FIG. 5;
  • FIG. 7 is a sectional view taken along line 7--7 of FIG. 4.
  • FIG. 1 there is depicted a test installation in a high pressure water system wherein a four inch steel high pressure supply line 10 is anchored in a concrete slab 12 and runs to a manually operable plug valve 14.
  • a four inch steel discharge or delivery line 16 is anchored in the concrete slab 12 at a distance from the supply line 10, and is connected to a similar plug valve 18, such that various apparatus can be connected between the plug valves 14 and 18 for testing and observation.
  • the plug valves serve to shut down and open up the system and, if desired, help provide resistance in the line for control purposes.
  • the outlet of the plug valve 14 at the high pressure supply is connected by means of a 4 inch to 2 inch reducer 20 to the inlet 22 of a control valve 24, which is a two inch Roto-Disc valve manufactured by Hitco, of Gardena, Calif, and generally described in U. S. Pat. No. 3,424,200.
  • the outlet 26 of the control valve is connected to the inlet of a ball canister 28, the outlet of which in turn is connected to the inlet of the discharge plug valve 18 by means of a 4 inch steel pipe section 30.
  • Intermediate support is provided by a pair of adjustable jacks 32, 34 having saddles 36, 38 respectively, shaped to fit under the flanges shown.
  • the control valve 24 includes an electric operator 40. While in actual tests on this system a manually actuated electric operator was used, conventional electric or hydraulic operators are available for responding to a hydraulic condition in the system to automatically control the degree of valve opening, and in FIG. 1 there is illustrated a water pressure sensing line 42 running from the operator 40 to a location downstream of the balls in the canister, and in this case actually running to a pressure tap 44 on the bottom of the outlet section of the canister itself. Normally severe cavitation will interfere with a pressure or flow measurement downstream from a control valve,
  • the ball canister is located downstream from the control valve in order that the maximum flow control at the valve be realized while suppressing cavitation at the valve.
  • the valve would have a very limited capability of controlling flow without being subjected to cavitation at high flow rates; but, with the canister located downstream of the valve, the canister provides sufficient back pressure on the valve such that higher flow velocities through the valve, hence higher pressure drops across the valve, can be realized without the valve being subjected to cavitation.
  • the distance of location of the canister downstream of the control valve can also be significant. Even aside from the obvious advantages of compactness of the system, convenience, and the desirability of using a short sensing line 42, under certain conditions a proximate location can be advantageous from the point of view of cavitation. From the latter point of view, if no cavitation is ever expected at the valve, the canister can be located at any convenient distance downstream of the valve. However, if some cavitation can be expected under certain flow conditions at certain degrees of valve opening, one would desire that the canister be located far enough downstream that the cavitation collapses before impinging upon the upstream layer of balls in the canister.
  • This distance is dependent upon the valve opening and normally varies between about two to five times the inside diameter of the control valve outlet 26, with the distance S being measured from the downstream end of the throat S0 of the valve to the upstream end of the balls in the canister.
  • the throat of a valve is considered to end and its outlet begin at the point where the throat constriction merges with the pipe like portion normally provided as an outlet, characteristic of conventional valves.
  • a relatively flat velocity profile normally requires at least about five diameters.
  • the canister should be close to the valve such that full development of the cavitation can not be realized due to the canister balls being interposed in the zone, thereby collapsing the super-cavitation before it can fully form and suppressing vibration.
  • a desirable distance S is about two internal diameters of the valve outlet.
  • the inlet and the first few upstream layers of balls be constructed of a highly erosion resistant material, such as stainless steel,
  • the case of the ball canister is of welded steel construction and includes a detachable inlet section 52, a conical or tapered section 54, a cylindrical retainer section 56, and an outlet section 58, with the direction of liquid flow being indicated by the arrows in the figure.
  • the detachable inlet section 52 has an upstream connecting flange 60, a downstream connecting flange 62, a smooth or streamlined two inch internal diameter neck or inlet 64, and a conically tapered throat 66 which merges smoothly and is streamlined with the downstream end of the neck 64.
  • the throat 66 of the inlet section extends downstream through the connecting flange 62 and terminates at the downstream end 69 of the conical section 54 so as to provide a smooth continuous cone, the diameter of which gradually increases in the downstream direction with the throat 66 defining the truncated apex of the cone.
  • the throat 66 in the inlet section contains the first or upstream four layers 71 of a volume of relatively small balls 70 which fill the conical section of the case and which are bare or exposed at the upstream end.
  • These first four layers of balls are nested and extend .flat across the case with the center line 72 of the first layer being located in the throat 66 at a position where the inside diameter of the throat D is of a predetermined value, and with the fourth or downstream layer being located approximately flush with the planar flange face 68 defining the downstream end of the throat.
  • the balls in the first four layers are welded or fused to one another and to the case, essentially in point to point contact so that there is no significant restriction of the passageways through the nested ball layers.
  • the conical case section 56 of the canister matches the conical throat 66 of the inlet section 52 to form a continuous truncated cone.
  • the conical section has a downstream connecting flange 78 to which the upstream flange 62 of the inlet section is detachably bolted, with a gasket 80 disposed between the abutting flange faces to seal them.
  • the conical section 54 expands to a predetermined diameter D, at its downstream end, such that the volume of balls 70 has a length L as measured between the center lines 72, 82 of its first and last ideally nested layers. Given predetermined upstream and downstream diameters D D,, the angle 0 of the cone is determined by the length L which is in turn determined by the number of nested layers of balls and the diameters of the balls.
  • the cylindrical retaining section 56 is welded to the downstream end of the conical case section 54, and is filled by a volume of larger retaining balls 84 tightly packed therein and in abutting relationship with the last or downstream layer of the relatively small balls 70.
  • the retaining balls 84 include a downstream or terminal layer of balls 86 which forms the base of a pyramidal nest 88 of retaining balls, welded together, centered within the volume of retaining balls 86, and pointing upstream.
  • a retainer plate 90 abuts the terminal layer 86 of retaining balls and has a hexagonal opening 92 centered therein.
  • a plurality of ribs 96 are welded in said opening and extend across said opening in spaced parallel relationship to divide the opening into a plurality of openings.
  • the retaining balls in the terminal layer 86 are tightly nested and fixed in a pattern which includes rows of adjacent balls having their center lines aligned with said ribs, as typically indicated at 96, with the balls in the row abutting the rib in point contact and being welded thereto. This provides solid support for the base layer 86 of the pyramidal stack of retaining balls 88, while providing a minimum of interference with liquid flow by preventing the balls from seating in the openings between the ribs.
  • a shoulder plate 98 abuts and is welded to the retainer plate 90 on its upstream side.
  • the shoulder plate 98 has a hexagonal opening 100 therein which is larger than and is aligned with the hexagonal opening 92 in the retainer plate 90, so as to form a peripheral shoulder 102 extending around the periphery of the hexagonal opening 92 on the upstream side of the retainer plate.
  • the terminal layer 86 of retaining balls is nested in a pattern which exactly fits the hexagonal opening 100 in the shoulder plate 98.
  • the shoulder plate and the retainer plate 90 form a dished grill matching the terminal layer 86 of retaining balls.
  • the retainer construction must be strong in order to prevent any balls from getting into the liquid flow system downstream, and at the same time should provide a minimum and known interference with liquid flow.
  • the retainer structure shown supports the downstream end of the volume of small balls 70, and provides a method whereby a retaining plate having a plurality of openings can be used without the problem of the small balls seating in or obstructing such openings and altering the flow characteristics, as is the case in conventional canister construction. Being held in position by the retaining balls in point to point contact therewith, the flow through the last layer of small balls is not substantially impeded nor are the balls able to reach an opening in the retainer plate.
  • the outlet section 58 includes a dished head I04 welded to the downstream end of the cylindrical retainer section 56.
  • a stub outlet 106 of 4 inch inside diameter is welded centrally to the dished head and carries a connecting flange 108 flush with its downstream end.
  • the canister includes a pressure tap 110 located upstream from the first layer of balls and communicating with the interior of the neck 64 of the inlet section.
  • a similar pressure tap 112 is located immediately downstream of the last layer of relatively small balls.
  • the other pressure tap 44 is located at the bottom of the outlet section 58 and communicates with the interior of the dished head 104, and the air tap 48 is located in the same position but on the opposite side of the canister of what would be the top side of the canister in operation since the air bubbles tend to collect at the top.
  • the pressure taps serve in conjunction with pressure gauges (not shown) to monitor pressures at strategic locations in the canister during operation to evaluate the performance of the canister under different flow conditions; or, as in the case of the downstream pressure outlet 44, they may serve control functions when connected to a hydraulic control device, such as to the control valve operator 40 by the pressure line 42.
  • the pressure tap 44 being located at the bottom also serves as a means of draining the canister. When not in use, the pressure taps and air tap would be plugged, for example as illustrated in FIG. 4.
  • loose retaining balls 113 are poured through the open upstream end 69 of the conical section 54 and surround the pyramidal stack 88.
  • the canister case is vibrated or struck with a hammer until the retaining balls become tightly packed and immobile.
  • the cylindrical section 54 is filled approximately flush with its upstream end, the 1% inch diameter balls 70 are poured into the open end of the conical base portion 54 and the case is again vibrated or struck with a hammer until these balls settle against the larger retaining balls and become tightly packed and immobile.
  • One-half inch diameter balls are added until they fill the conical case portion 54 and reside approximately flush with its open upstream end, after which the detachable inlet section 52 containing the first four layers of welded balls is attached by bolting its downstream flange into the upstream flange of the conical section 54.
  • the relatively large retaining balls 84 and the relatively small balls 70 will not reside entirely in nested layers as shown in FIG. 4 merely for purpose of illustration, except where they are welded together.
  • the small and large balls will settle into some of the void areas shown around the perimeter of the layers in FIG. 4, or the layers will spread to fill some of these voids, and some of the small balls may enter certain adjacent void areas in the volume of larger balls, as illustrated for example at 116, 118. Nevertheless, the balls both in the conical and retaining section will approximate layers, and are tightly packed and immobile.
  • the relatively small balls filling the conical portion of the canister should have a diameter which is relatively small compared to the diameter of the case so that many balls are required to form a given layer filling a cross-section of the case. Seven nested balls in a layer probably would be sufficient, but in our test canister we used nineteen for the upstream layer at a position where the case diameter D was 2.7 inches. We believe that the balls should be as small as practicable consistent with their not acting as a strainer, such that the passageways between the balls tend to be clogged by deposits from the liquid medium flowing through them, and consistent with keeping the cone angle 0 small.
  • the small balls 70 should be approximately spherical and ideally should be constructed of a very hard material highly resistant to erosion and to corrosion by the liquid medium. While we have used cast iron grinding balls in our tests due to their low cost and ready availability, and while these balls would render acceptable performance in many liquid system applications consistent with replacement costs, better balls are available such as rejected stainless steel ball bearings or ceramic grinding balls such as those available from Coors Porcelain Company of Golden, Colo. for which there are methods of welding and fusing the balls together and to the case without significantly reducing the passageways through the ball areas.
  • the major variables will be variations in pressure and flow rates and, where a given control valve is used in conjunction with the canister, changes in the degree of valve opening.
  • the upstream pressure is known and is approximately constant, and system is designed to deliver a maximum volume flow rate at a much lower downstream pressure while controlling or repressing cavitation.
  • the next design consideration is to select a control valve all of the components of which are of adequate pressure rating to accommodate the maximum working pressure with a safety factor, and with the valve having a high velocity rating so as to minimize the size of valve required to obtain the maximum flow rate, thereby normally to minimize the cost of the valve and its appurtenances.
  • Many valves are not constructed to operate at a water velocity of 81.5 feet per second. The flow-through" type valve normally is best in this regard.
  • flow-through refers to the type of valve where the stream passes through the valve in a substantially straight path as opposed to a tortious path, and where, when the valve is wide open, it essentially provides no constriction and matches the pipe. Also, the flow-through type valve generally will handle higher liquid velocities without cavitation at a given operating pressure.
  • a good example of such a valve is the Hitco Roto-Disc valve illustrated in FIG. I having a 2 inch internal diameter throat 50 which matches the pipe when wide open.
  • valve type and size which will provide the desired flow rate at high velocity, is that the liquid velocity issuing from the valve outlet should be near the critical cavitation velocity of the liquid at the operating pressure at the first layer of balls in the canister in order to take full advantage of the maximum energy which can be dissipated by the first layer of balls without cavitation, so that a minimum of reductions or increases in the internal diameter of the inlet section of the canister or other pipe upstream from the first ball layer is required to achieve such velocity.
  • the next step normally to be employed in design is the determination of the size of balls to be used and the size of the canister portion containing the balls.
  • Ball size has already been discussed; hence, using /2 inch spheres in our test canister, the exercise was to calculate the diameter D,, at the upstream layer of balls, the diameter D,, at the downstream layer of balls, and the length L required to achieve the desired pressure reduction at maximum flow rate.
  • FIG. 3 generally illustrates such a laboratory determination.
  • a sensor such as an accelerometer
  • the sensor output will increase as the liquid flow velocity is increased at constant pressure, the measurement normally being made by measuring the liquid velocity upstream of the orifice at constant upstream pressure with changes in flow velocity being obtained by adjusting the downstream pressure, although the measurement can be made in a reverse fashion at least for purposes of determining incipient cavitation.
  • the sensor output will first gradually increase on account of increasing flow noise until a point is reached where the sensor output begins to rise rapidly, this being the point of incipient cavitation with the flow velocity at this point being referred to as the critical cavitation velocity, V Further in crease in the flow velocity will result in a rapidly increasing level of cavitation and finally, if there is sufficient energy in the system, in super-cavitation where, if the cavitation collapses some distance downstream, the sensor output may and frequently does decline somewhat because of its more remote location from the area of collapse.
  • Critical cavitation velocity will vary with pressure, and it is found that the point of incipient cavitation will occur at lesser velocities as the local pressure is reduced.
  • the critical cavitation velocity of the upstream layer of balls at a local pressure of about 660 psig. was estimated to be about 41 feet per second, based on previous laboratory experience.
  • the critical cavitation velocity was estimated to be about 7.2 feet per second as measured in the stream issuing from the last layer at an assumed local pressure of 20 psig.
  • the upstream diameter D should be about 2.7 inches and the downstream diameter D, should be about 6.7 inches.
  • N The number of layers of small balls, equal to L divided by 0.866 d L
  • the energy equation indicates a pressure drop of 653.5 psi across the volume of small balls in the canister.
  • the summation was solved as an iteration by assuming various values for L which resulted in an integer value for N, the number of ball layers, until a correct value was found which caused the summation of pressure drops across the successive layers to add up to the 653.5 psi pressure drop calculated across the ball volume indicated at the left side of the equation.
  • test canister was constructed in accordance with the above calculations and it worked remarkably well considering that we ignored the pressure drop across the retainer and outlet section of the canister, which should be added to the right side of the energy equation to valuate whole canister operation. As measured this pressure drop turned out to be about psi. The performance seemed remarkable for other reasons as well, such as the matter of assuming critical cavitation velocities from previous laboratory experience rather than actually measuring them at the laboratory.
  • P and P were both assumed as constant at about 660 psig. with the control valve 100 percent open. P actually varied from about 720 psig. to about 674 psig. as the valve was opened from 5 to 100 percent open, with P varying accordingly from about 20 psig. to 24 psig.
  • ball constant K was determined from the measurements made on 1% inch cast iron grinding balls tightly packed in a 4 inch diameter cylinder, and we are uncertain as to whether the ball constant K might vary from layer to layer depending upon the diameter of the balls and the diameter of the canister at the layer. Of course, these factors can be measured in the laboratory although we have not yet done so sacred.
  • the cylindrical canister case might require between 600 and 700 such layers of balls to achieve the same pressure drop, as compared to the mere 30 layers of balls required by the conical canister, when both operate at the same cavitation intensity.
  • FIG. 2 is a graph illustrating P as actually measured at different degrees of valve opening.
  • P was measured at the longitudinal position indicated in FIG. 1 and was a measure of the downstream pressure on the valve or the upstream pressure on the canister, both being roughly the same. Also, the measured volume flow rates in gallons per minute corresponding to various points on the curve are shown in the figure.
  • the pressure differential across the valve (P P as well as the pressure differential across the canister (P P are only approximate from the figure because the mentioned minor variations in the upstream and downstream pressures are not taken into account.
  • the system illustrated in FIG. 1 was instrumented with accelerometers (not shown), and with pressure gauges (not shown) at various locations including the longitudinal positions indicated at P P and P Flow measurements were made downstream of the canister.
  • the accelerometer readings remained in the vicinity of l0,000 to 20,000 inches/sec. peak to peak, except in the 20 to 25 percent valve opening range where some readings approached 50,000 to l00,000 inches/see, which appears to be about the percentage valve opening where about half the pressure drop in the system was across the canister, and indicates the possible presence of some fine-grained cavitation at the valve. Also, large quantities of air were discharged through the orifice 48.
  • the system was otherwise a supercavitating liquid flow system.
  • the pressure measured at the valve outlet varied from a vacuum of 9 inches of mercury at a 15 percent valve opening to a vacuum of 17 inches of mercury at a 40 percent valve opening, with the flow rates varying from 445 gallons per minute to 937 gallons per minute at these openings.
  • the vibration and noise level was so great in the vicinity that it was not considered safe or desirable to maintain the valve open at 40 percent or to open it further.
  • valve opening such as say 30 percent open
  • the valve could then be opened 100 percent to cause a sufficiently excessive flow rate and pressure drop across the canister to cause cavitation in the canister in order to clean it of any scale or deposits.
  • a system for supplying the liquid at a relatively low pressure from a high pressure supply while repressing cavitation in the liquid comprising a control valve having an operator for opening and closing the valve to varying degrees to vary the liquid volume flow rate through the valve, means coupling the inlet of the control valve to the high pressure supply, a canister, and means coupling the inlet of the canister to the outlet of the control valve, said canister including a case, a volume of balls filling the case along a portion of the length thereof, and means retaining the balls in the case, with the diameter and length of said ball filled case portion being sized to significantly repress cavitation at the control valve over a range of volume flow rates which includes the designed maximum flow rate of the system.
  • a system for supplying the liquid at a relatively low pressure from a high pressure supply while repressing cavitation in the liquid comprising a control valve having an operator for opening and closing the valve to varying degrees to vary the liquid volume flow rate through the valve, means coupling the inlet of the control valve to the high pressure supply, a canister, and means coupling the inlet of the canister to the outlet of the control valve, said canister including a case, a volume of balls filling the case along a portion of the length thereof, and means retaining the balls in the case, with the diameter and length of said ball filled case portion being sized to significantly repress cavitation at the control valve over a range of volume flow rates which includes the designed maximum flow rate of the system, with the diameter of the canister case at the upstream end of the ball volume being sufficiently small to present a liquid velocity near the incipient cavitation velocity at that location at the maximum designed volume flow rate of the system, and wherein the canister case increases in diameter going downstream.
  • a system for supplying liquid at a relatively low pressure from a high pressure supply while repressing cavitation in the liquid comprising a control valve, means for coupling the inlet of the control valve to the high pressure supply, a canister, and means coupling the inlet of the canister to the outlet of the control valve, said canister including a case, a volume of balls filling the case along a portion of the length thereof, and means retaining the balls in the case, with the diameter and length of said ball filled case portion being sized to significantly repress cavitation at the control valve over a range of volume flow rates which includes the designed maximum flow rate of the system, with the diameter of the canister case at the upstream end of the ball volume being sufficiently small to present a liquid velocity near the incipient cavitation velocity at that location at the maximum designed volume flow rate of the system, and wherein the canister case increases in diameter going downstream, and wherein the system is sized to accommodate the maximum designed volume flow rate when the valve is only partially open, whereby the valve may be opened further to
  • a system for supplying liquid at a relatively low pressure from a high pressure supply while repressing cavitation in the liquid comprising a control valve, means for coupling the inlet of the control valve to the high pressure supply, a canister, and means coupling the inlet of the canister to the outlet of the control valve, said canister including a case, a volume of balls filling the case along a portion of the length thereof, and means retaining the balls in the case, with the diameter and length of said ball filled case portion being sized to significantly repress cavitation at the control valve over a range of volume flow rates which includes the designed maximum flow rate of the system, and wherein the upstream end of the ball volume is disposed downstream of the throat of the control valve a distance which is equal to about two to five times the inside diameter of the control valve outlet.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Details Of Valves (AREA)
  • Treatment Of Fiber Materials (AREA)
  • Check Valves (AREA)
  • Pipe Accessories (AREA)
US00095044A 1970-12-04 1970-12-04 Ball canister and system for controlling cavitation in liquids Expired - Lifetime US3731903A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US9504470A 1970-12-04 1970-12-04

Publications (1)

Publication Number Publication Date
US3731903A true US3731903A (en) 1973-05-08

Family

ID=22248954

Family Applications (1)

Application Number Title Priority Date Filing Date
US00095044A Expired - Lifetime US3731903A (en) 1970-12-04 1970-12-04 Ball canister and system for controlling cavitation in liquids

Country Status (6)

Country Link
US (1) US3731903A (enrdf_load_stackoverflow)
JP (1) JPS5210522B1 (enrdf_load_stackoverflow)
CA (1) CA966394A (enrdf_load_stackoverflow)
DE (1) DE2159963C3 (enrdf_load_stackoverflow)
GB (1) GB1356318A (enrdf_load_stackoverflow)
IL (1) IL38292A (enrdf_load_stackoverflow)

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2410231A1 (de) * 1974-03-04 1975-09-18 Max Planck Gesellschaft Schwingungsarmes, insbesondere geraeuscharmes stroemungsorgan, insbesondere drosselorgan
US4007908A (en) * 1975-05-09 1977-02-15 Masoneilan International, Inc. Process and device for attenuating noise caused by a valve during the expansion of a fluid
US4180100A (en) * 1976-05-22 1979-12-25 Bayer Aktiengesellschaft Control valve having a low noise throttling device
US4398563A (en) * 1981-09-28 1983-08-16 Vacco Industries Multi-tube flow restrictor
US20080237516A1 (en) * 2004-01-12 2008-10-02 Baldwin Jimek Ab Sensing Device
WO2013138092A3 (en) * 2012-03-14 2014-04-10 T-3 Property Holdings, Inc. Reduced cavitation oilfield choke
CN105003736A (zh) * 2014-04-22 2015-10-28 艾默生过程管理调节技术公司 用于流体传输线的声音处理组件
RU184843U1 (ru) * 2018-04-06 2018-11-12 Федеральное государственное бюджетное образовательное учреждение высшего образования "Кубанский государственный технологический университет" (ФГБОУ ВО "КубГТУ") Устройство для гашения гидравлического удара

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2422108C2 (de) * 1974-05-08 1983-07-28 Willi Daume, Regelarmaturen, 3000 Hannover Drosseleinrichtung mit Schallunterdrückung
JPS5414724U (enrdf_load_stackoverflow) * 1977-07-04 1979-01-30
DE3428540A1 (de) * 1984-08-02 1986-02-13 Siekmann, Helmut E., Prof.Dr.-Ing., 1000 Berlin Vorrichtung zur erzeugung von kavitation

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB189824148A (en) * 1898-11-16 1899-09-23 Daniel Hurst Improved Means for Controlling the Flow of Fluids Under Pressure.
GB112980A (en) * 1917-01-30 1918-01-30 Willans And Robinson Ltd Improvements in connection with Supplying Compressed Air to the Cylinders of Internal Combustion Engines.
US2323839A (en) * 1941-01-27 1943-07-06 Jeddy D Nixon Fluid flow control device
DE1063432B (de) * 1955-05-28 1959-08-13 Siemens Ag Druckreduzierventil zur geraeusch- und vibrationsarmen Drosselung stroemender, gasfoermiger Medien, insbesondere zur Druckreduzierung von Dampf
DE1067652B (de) * 1955-05-28 1959-10-22 Siemens Ag Druck-Reduzierventil zur geraeusch- und vibrationsarmen Drosselung stroemender gasfoermiger Medien, insbesondere zur Druckreduzierung von Dampf
DE1094542B (de) * 1955-05-31 1960-12-08 Heinz Mika Einrichtung zur Drosselung gasfoermiger Mittel, insbesondere von Dampf

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB189824148A (en) * 1898-11-16 1899-09-23 Daniel Hurst Improved Means for Controlling the Flow of Fluids Under Pressure.
GB112980A (en) * 1917-01-30 1918-01-30 Willans And Robinson Ltd Improvements in connection with Supplying Compressed Air to the Cylinders of Internal Combustion Engines.
US2323839A (en) * 1941-01-27 1943-07-06 Jeddy D Nixon Fluid flow control device
DE1063432B (de) * 1955-05-28 1959-08-13 Siemens Ag Druckreduzierventil zur geraeusch- und vibrationsarmen Drosselung stroemender, gasfoermiger Medien, insbesondere zur Druckreduzierung von Dampf
DE1067652B (de) * 1955-05-28 1959-10-22 Siemens Ag Druck-Reduzierventil zur geraeusch- und vibrationsarmen Drosselung stroemender gasfoermiger Medien, insbesondere zur Druckreduzierung von Dampf
DE1094542B (de) * 1955-05-31 1960-12-08 Heinz Mika Einrichtung zur Drosselung gasfoermiger Mittel, insbesondere von Dampf

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2410231A1 (de) * 1974-03-04 1975-09-18 Max Planck Gesellschaft Schwingungsarmes, insbesondere geraeuscharmes stroemungsorgan, insbesondere drosselorgan
US4007908A (en) * 1975-05-09 1977-02-15 Masoneilan International, Inc. Process and device for attenuating noise caused by a valve during the expansion of a fluid
US4180100A (en) * 1976-05-22 1979-12-25 Bayer Aktiengesellschaft Control valve having a low noise throttling device
US4398563A (en) * 1981-09-28 1983-08-16 Vacco Industries Multi-tube flow restrictor
US20080237516A1 (en) * 2004-01-12 2008-10-02 Baldwin Jimek Ab Sensing Device
WO2013138092A3 (en) * 2012-03-14 2014-04-10 T-3 Property Holdings, Inc. Reduced cavitation oilfield choke
US9611952B2 (en) 2012-03-14 2017-04-04 National Oilwell Varco, L.P. Reduced cavitation oilfield choke
CN105003736A (zh) * 2014-04-22 2015-10-28 艾默生过程管理调节技术公司 用于流体传输线的声音处理组件
US9587765B2 (en) 2014-04-22 2017-03-07 Emerson Process Management Regulator Technologies, Inc. Sound treatment assembly for a fluid transmission line
CN105003736B (zh) * 2014-04-22 2020-01-10 艾默生过程管理调节技术公司 用于流体传输线的声音处理组件
RU184843U1 (ru) * 2018-04-06 2018-11-12 Федеральное государственное бюджетное образовательное учреждение высшего образования "Кубанский государственный технологический университет" (ФГБОУ ВО "КубГТУ") Устройство для гашения гидравлического удара

Also Published As

Publication number Publication date
DE2159963C3 (de) 1978-11-30
CA966394A (en) 1975-04-22
IL38292A (en) 1974-12-31
DE2159963B2 (de) 1978-03-23
DE2159963A1 (de) 1972-06-29
JPS5210522B1 (enrdf_load_stackoverflow) 1977-03-24
IL38292A0 (en) 1972-02-29
GB1356318A (en) 1974-06-12

Similar Documents

Publication Publication Date Title
US3866630A (en) Ball canister and system for controlling cavitation in liquids
US3731903A (en) Ball canister and system for controlling cavitation in liquids
Ohrn et al. Geometrical effects on discharge coefficients for plain-orifice atomizers
US5596152A (en) Flow straightener for a turbine-wheel gasmeter
US3921672A (en) Choke for controlling flow of pressurized fluid
RU2491513C2 (ru) Усредняющая диафрагма с отверстиями, расположенными рядом с внутренней стенкой трубы
US10989328B2 (en) Erosion monitoring system
US20110146811A1 (en) Air release valve
US5255716A (en) Pipe rectifier for stabilizing fluid flow
EP3762686B1 (de) Fluiddurchflussmesser
EP2482046B1 (de) Vorrichtung zur Ermittlung eines Füllstandes eines Mediums
US3771550A (en) Ball canister and system for controlling cavitation in liquids
EP2452109A1 (en) Control valve having pressure boundary integrity diagnostic capabilities, method of making the control valve, and method of using the control valve
Banks et al. Experimental study of the impingement of a liquid jet on the surface of a heavier liquid
Prabu et al. Effects of upstream pipe fittings on the performance of orifice and conical flowmeters
Azad et al. New method of obtaining dissipation
US9995614B2 (en) Fluid flow rate measuring device including a diverting unit for diverting the flow into a measuring section
DE102008035349B4 (de) Anlage und Verfahren zur Abgabe von Flüssigkeit aus einem mehrere Kammern enthaltenden Tankwagen durch Schwerkraft
Wang et al. Initial dilution of a vertical round non-buoyant jet in wavy cross-flow environment
CA2991568C (en) Real-time erosion control in flow conduits
US3753529A (en) Spray apparatus
US20210333138A1 (en) Water meter assembly with taper for minimizing head loss
Ramamurthi et al. Hysteresis and bifurcation of flow in fuel injection nozzles
Stevens et al. Vortex flow through horizontal orifices
CN219464714U (zh) 一种超快冷喷水箱及超快冷装置